Intake-air cooling type gas turbine power equipment and combined power plant using same

ABSTRACT

In an intake-air refrigeration system of intake-air cooling type gas turbine power equipment, heat discharged to the atmosphere heretofore is recovered for further utilization. A refrigerant vapor discharged from an evaporator ( 05 ) of the refrigeration system is compressed by a refrigerant compressor ( 02 ) to be transformed to pressurized refrigerant vapor. Heat carried by the pressurized refrigerant vapor is supplied to a heat utilization system ( 80 ) to be recovered therein.

BACKGROUND OF THE INVENTION

[0001] 1. Field of the Invention

[0002] The present invention relates to intake-air cooling type gasturbine power equipment. More particularly, the invention is concernedwith intake-air cooling type gas turbine power equipment in which airtaken in from the atmosphere is previously cooled and then the cooledair is compressed to produce compressed air, which is then subjected tocombustion with a fuel introduced from an external system providedseparately from the power equipment, wherein a gas turbine isrotationally driven under the action of the combustion gas of a hightemperature resulting from the combustion of the compressed air with thefuel supplied from the external system, and wherein an electricgenerator operatively coupled to a rotor shaft of the gas turbine isdriven through rotation of the rotor shaft for generating electricenergy.

[0003] Furthermore, the present invention is also concerned with acombined power plant comprised of a combination of the gas turbine powerequipment described above and steam turbine power generation equipmentwhich includes a heat-recovery type steam generation boiler in whichheat carried by an exhaust gas discharged from the gas turbine isrecovered to be utilized for producing a high-temperature/high-pressuresteam, a steam turbine driven under the action of thehigh-temperature/high-pressure steam produced by the heat-recovery typesteam generation boiler, and an electric generator operatively coupledto a rotor shaft of the steam turbine, wherein the electric generator isdriven through rotation of the rotor shaft for generating electricenergy.

[0004] 2. Description of Related Art

[0005] In the conventional gas turbine equipment, air is taken in fromthe atmosphere for combustion with a fuel within a combustor or forcooling high-temperature components of the gas turbine equipment whichare heated to high-temperatures in the course of operation of the gasturbine equipment such as, for example, the main body of the combustor,a tail cylinder, moving blades and stationary blades of the first stageas well as a blade shroud of the gas turbine. The air taken in, i.e.,the intake air, is compressed by an air compressor for producingcompressed air which is then supplied to the combustor or fed to theaforementioned high-temperature components of the gas turbine equipmentfor the cooling thereof.

[0006] In recent years, with a view to increasing the output of the gasturbine equipment by combusting a greater amount of fuel whileincreasing the amount of intake air so that a greater amount of air canbe used for cooling the high-temperature components of the equipment tothereby reduce heat load thereof for allowing the manufacturing costs ofthe high-temperature components to be decreased while lengthening theservice life thereof, and additionally for the purpose of increasing theinlet temperature of the gas turbine, there has been developed the gasturbine equipment which adopts such an intake air cooling scheme thatthe air taken in from the atmosphere, i.e., the intake air of the gasturbine, is cooled in precedence to being supplied to the aircompressor, whereon the cooled air is introduced into the gas turbineequipment to thereby increase the effective air quantity, i.e., massflow of air. Such gas turbine equipment is now attracting publicattention.

[0007] As one of the means for cooling the intake gas of the gasturbine, there is known a refrigeration system. FIG. 15 is a blockdiagram showing schematically an arrangement of a conventionalrefrigeration system. Referring to the figure, reference numeral 101denotes an electric drive motor, 102 denotes generally a refrigerantcompressor driven by the electric motor 101 for compressing arefrigerant vapor to thereby produce a compressed refrigerant vapor, 103denotes a condenser for cooling the compressed refrigerant vapor withcooling water to condense the compressed refrigerant vapor for therebyproducing a liquid-phase refrigerant or refrigerant liquid, 104 denotesa cooling tower for cooling the water which is heated upon cooling ofthe compressed refrigerant vapor and for feeding back the cooled waterto the condenser 103, and 104′ denotes an additional cooling apparatuswhich is installed separately from the cooling tower 104 and which isdestined for cooling the water heated in the condenser 103 and feedingback the cooled water to the latter. Further, reference numeral 105denotes an evaporator for expanding the refrigerant liquid to transformit to the gas phase, i.e., refrigerant vapor. In that case, watercirculating through or between a destined cooling water utilizationsystem (not shown) and the evaporator 105 is deprived of a quantity ofheat which corresponds to the latent heat of vaporization of therefrigerant liquid upon expansion thereof. In this way, the circulatingwater is cooled before being supplied to the destined cooling waterutilization system.

[0008] In operation, the refrigerant compressor 102 is driven by theelectric motor 101 to compress the refrigerant vapor, e.g. vapor ofsubstitute freon, ammonia or the like. The compressed refrigerant vaporis then charged to the condenser 103 where the compressed refrigerantvapor is cooled by the cooling water fed from the cooling tower 104and/or the additional cooling apparatus 104′ to be condensed to therefrigerant liquid (i.e., liquid-phase refrigerant) which is then fed tothe evaporator 105. As mentioned above, water is circulating through theevaporator 105 and the cooling water utilization system (not shown).Consequently, in the evaporator 105, the circulating water is deprivedof heat equivalent or corresponding to the latent heat of vaporizationof the refrigerant liquid, which is thus vaporized or gasified into therefrigerant vapor. On the other hand, the circulating water deprived ofheat equivalent to the latent heat of vaporization of the refrigerantliquid is cooled and fed to the cooling water utilization system orequipment. The refrigerant vapor is supplied to the refrigerantcompressor 102 and compressed again to be discharged therefrom as thecompressed refrigerant vapor. In this way, a refrigeration cycle isestablished through the processes of heat transfers to/from therefrigerant and the phase changes or transformations thereof.

[0009] In the refrigeration cycle described above, the amount of heatinjected into the refrigeration system is a sum of the heat Q1 which isgenerated upon compression of the refrigerant vapor in the refrigerantcompressor 102 which is driven by the electric motor (i.e., heatcorresponding to the driving energy for the electric motor) and the heatQ2 which is equivalent to the latent heat of vaporization deprived ofthe water circulating through the evaporator 105 and the destinedcooling water utilization system. On the other hand, heat emanating fromthe refrigeration system to the ambient is represented by the heat Q3which is dissipated from the cooling tower 104 and the additionalcooling apparatus 104′ when water whose temperature has been raised uponcooling of the compressed refrigerant vapor in the condenser 103 forcondensation thereof to the liquid phase is cooled to cold water in thecooling tower 104 and/or the additional cooling apparatus 104′. The heatinjected into the refrigeration system and the heat dissipated therefrommust be in equilibrium with each other. In other words, there appliesvalid the relation given by Q3=Q1+Q2.

[0010]FIG. 16 is a block diagram showing a system configuration of aconventional intake-air cooling type gas turbine power equipment inwhich a refrigeration system is employed. Referring to FIG. 16,reference numeral 106 denotes generally a refrigeration system whichincludes as major components an electric motor 101, a refrigerantcompressor 102, a condenser 103, a cooling tower 104 and an evaporator105. Reference numeral 107 designates air in the atmosphere. Further,reference numeral 108 denotes a suction chamber into which the air 107is introduced, 109 designates feed air discharged from the suctionchamber, 110 denotes an intake-air cooling chamber for cooling the feedair 109 discharged from the suction chamber 108 through heat exchangewith the water cooled by the evaporator 105 of the refrigeration system106, numeral 111 designates cooled air which is cooled in the intake-aircooling chamber and exhibiting an increased mass flow, 112 denotes anair compressor for transforming the cooled air 111 into compressed air,113 designates flow of the compressed air compressed by the aircompressor (to be utilized for the fuel combustion and for cooling thehigh-temperature components), 114 designates a fuel supplied from arelevant system (not shown), 115 denotes a combustor for combusting thecompressed air 113 and the fuel 114 to thereby produce ahigh-temperature combustion gas, 116 designates a flow of thehigh-temperature combustion gas produced by the combustor 115, numeral117 denotes a gas turbine driven rotationally under the action of thehigh-temperature combustion gas 116, numeral 118 denotes an electricgenerator which is operatively coupled to a rotor shaft of the gasturbine and driven through rotation of the rotor shaft for therebygenerating electric energy.

[0011] In the refrigeration system 106, the refrigerant vapor, e.g. gasof substitute freon, ammonia or the like, is compressed by therefrigerant compressor 102 driven by the electric drive motor 101 andthen supplied to the condenser 103 where the compressed refrigerantvapor is cooled by the cold water fed from the cooling tower 104 to becondensed into a refrigerant liquid. The refrigerant liquid undergoesphase-transformation into a refrigerant vapor in the evaporator 105.Upon phase-transformation of the refrigerant liquid in the evaporator105, heat corresponding to the latent heat of vaporization is deprivedof from the water circulating through the evaporator 105 and theintake-air cooling chamber 110, whereby the circulating water is cooledto cold water. On the other hand, air 107 is introduced into the suctionchamber 108 from the atmosphere as the gas turbine intake air, and thusthe feed air 109 is supplied to the intake-air cooling chamber 110 fromthe suction chamber 108. In the intake-air cooling chamber 110, the feedair 109 is cooled by the cold water supplied from the evaporator 105,whereby the cooled air 111 is discharged from the intake-air coolingchamber 110. The water whose temperature has been raised upon cooling ofthe feed air 109 is fed back to the evaporator 105 to be cooled again toserve as the cooling water. The cooled air 111 is fed to the aircompressor 112 to be compressed. Thus, the compressed air 113 isdischarged from the air compressor 112. A major portion of thecompressed air 113 is supplied to the combustor 115 to undergocombustion with the fuel 114 fed from a fuel system (not shown). On theother hand, the remaining part of the compressed air 113 is made use offor cooling the high-temperature components of the gas turbine powerequipment. The high-temperature combustion gas 116 which results fromthe combustion of the fuel 114 with the air in the combustor 115 is fedto the gas turbine 117. Under the action of the high-temperaturecombustion gas 116, the moving blades mounted fixedly on a rotor (notshown) of the gas turbine 117 are caused to rotate at a high speed.Thus, the electric generator 118 operatively coupled to the rotor shaftof the turbine is rotationally driven for generation of the electricenergy.

[0012]FIG. 17 is a block diagram showing schematically and generally asystem configuration of a combined power plant in which the intake-aircooling type gas turbine power equipment described above by reference toFIG. 16 is combined with a heat-recovery type steam generation boilerand steam turbine power generating equipment with a view to enhancingthe efficiency of power generation. In the figure, reference numeral 119designates an exhaust gas discharged from the gas turbine 117, numeral120 denotes a heat-recovery steam generation boiler for recovering theheat carried by the exhaust gas 119 to thereby produce ahigh-temperature/ high-pressure steam by burning a fuel supplied to theboiler, as occasion requires, 121 designates a flow ofhigh-temperature/high-pressure steam 21 produced by the heat-recoverytype steam generation boiler 120, numeral 122 denotes a steam turbinerotated under the action of the high-tempera-ture-high-pressure steam121, numeral 123 denotes an electric generator which is operativelycoupled to a rotor shaft of the steam turbine and driven throughrotation of the rotor shaft thereof for generating electric energy, 124designates a flow of exhaust steam discharged from the steam turbine 22,numeral 125 denotes a condenser for condensing the exhaust steam 124into condensed water, 126 designates a flow of condensed water which isfed back to the heat-recovery type steam generation boiler, andreference symbol P1 denotes a pump for feeding the condensed water 126to the heat-recovery type steam generation boiler 120. Further,reference numeral 127 designates a flow of exhaust gas discharged fromthe heat-recovery type steam generation boiler 120, and numeral 128denotes a smoke stack for discharging the exhaust gas 127 to theatmosphere.

[0013] In the figures referenced in the above and in the followingdescription, thick solid lines indicate flows of intake air and exhaustgases in the gas turbine power equipment and the heat-recovery typesteam generation boiler, thin solid lines indicate flows of water,refrigerant liquid and the like, and broken lines indicate flows ofgases such as steam, refrigerant vapor and the like which circulatethrough or between the refrigeration system and the steam turbine powergeneration equipment.

[0014] In the intake-air cooling type gas turbine power equipment shownin FIG. 16 as well as in the combined power plant including thecombination of the intake-air cooling type gas turbine power equipment,the heat-recovery type steam generation boiler and the steam turbinepower generation equipment, as shown in FIG. 17, it is noted that in therefrigeration system designed for cooling the gas turbine intake air asdescribed hereinbefore by reference to the block diagram of FIG. 15showing the system configuration of the refrigeration system, the heatquantities (Q1+Q2) injected into the refrigerant circulating system ofthe refrigeration system 106 comprised of the refrigerant compressor102, the condenser 103, the evaporator 105 and so forth, i.e., the sumof the heat Q1 generated upon compression of the refrigerant vapor bythe refrigerant compressor 102 driven by the electric motor 101 and theheat Q2 recovered from the water circulating through the evaporator 105and the intake-air cooling chamber 110, namely, the heat substantiallyequivalent to the heat recovered, being deprived of from the feed air109 (i.e., the intake air of the gas turbine) upon cooling thereof, istransmitted to the water circulating through the condenser 103 and thecooling tower 104 and/or the additional cooling apparatus 104′ to beultimately dissipated from the cooling tower and/or the other coolingapparatus to the atmosphere, involving thus a heat loss.

SUMMARY OF THE INVENTION

[0015] In the light of the state of the art described above, it is anobject of the present invention to provide intake-air cooling type gasturbine power equipment and a combined power plant comprised of acombination of the intake-air cooling type gas turbine power equipmentwith a heat-recovery type steam generation boiler and steam turbinepower generation equipment in which the heat dissipated to theatmosphere in the conventional intake-air cooling type gas turbine powerequipment and the conventional combined power plant is recovered forutilization as heat source for generation of steam in the electric powergeneration systems, heat source for reheating the intake air of the gasturbine after having been cooled as well as for utilization in a heatutilization system such as a thermal process or processes, an energyservice center and/or the like while suppressing the heat loss to apossible minimum.

[0016] In view of the above and other objects which will become apparentas the description proceeds, the present invention is directed toimprovement of the intake-air cooling type gas turbine power equipmentand the combined power equipment including a combination of theintake-air cooling type gas turbine power equipment, a heat-recoverytype steam generation boiler and steam turbine power generationequipment.

[0017] Thus, according to a general aspect of the present invention,there is provided intake-air cooling type gas turbine power equipment,which includes a refrigeration system comprised of an evaporator and arefrigerant compressor, an intake-air cooling chamber for cooling airtaken in from the atmosphere by the evaporator of the refrigerationsystem, an air compressor for compressing the air cooled in theintake-air cooling chamber to thereby produce compressed air, acombustor for burning a fuel supplied from an external system with thecompressed air produced by said air compressor to thereby produce acombustion gas, a gas turbine driven rotationally under the action ofthe combustion gas produced by the combustor, and an electric generatoroperatively coupled to a rotor shaft of the gas turbine for generatingelectric energy, being driven through rotation of the rotor shaft,wherein the refrigerant vapor leaving the evaporator of therefrigeration system is compressed by means of the aforementionedrefrigerant compressor to be transformed to a pressurized refrigerantvapor, and wherein heat carried by the pressurized refrigerant vapor issupplied to a heat utilization system to be recovered for utilization.

[0018] In a preferred mode for carrying out the present invention, thepressurized refrigerant vapor itself that leaves the refrigerantcompressor may be circulated through the heat utilization system so thatthe heat carried by the pressurized refrigerant vapor can be supplied tothe heat utilization system for recovery.

[0019] In another preferred mode for carrying out the invention, therefrigeration system may further include a condenser, wherein thepressurized refrigerant vapor leaving the refrigerant compressor is fedto the condenser so that the pressurized refrigerant vapor can undergoheat exchange with a heat transfer medium which circulates through thecondenser and the heat utilization system, whereby heat carried by thecompressed refrigerant vapor is supplied to the heat utilization systemthrough the medium of the heat transfer medium to be recovered forutilization in the heat utilization system.

[0020] In yet another preferred mode for carrying out the invention, aheater for heating and drying the air cooled by the intake-air coolingchamber may be disposed within the intake-air cooling chamber at acooled-air discharge side thereof, and the heat carried by thepressurized refrigerant vapor leaving the refrigerant compressor may beutilized as a source of heat for the heater.

[0021] According to another aspect of the invention, there is provided acombined power plant, which includes intake-air cooling type gas turbinepower equipment, a heat-recovery type steam generation boiler, steamturbine power generation equipment and a condenser. In the combinedpower plant, the intake-air cooling type gas turbine power equipmentincludes a refrigeration system comprised of an evaporator and arefrigerant compressor, an intake-air cooling chamber for cooling airtaken in from the atmosphere by the evaporator of the refrigerationsystem, an air compressor for compressing the air cooled by theintake-air cooling chamber to thereby produce compressed air, acombustor for burning a fuel supplied from an external system with thecompressed air produced by said air compressor to thereby produce acombustion gas, a gas turbine driven rotationally under the action ofthe combustion gas produced by the combustor, and an electric generatoroperatively coupled to a rotor shaft of the gas turbine for generatingelectric energy, being driven through rotation of the rotor shaft. Theheat-recovery type steam generation boiler mentioned above serves forrecovering a quantity of heat carried by the combustion exhaust gasdischarged from the gas turbine of the gas turbine power equipment. Onthe other hand, the steam turbine power generation equipment mentionedabove includes a steam turbine driven rotationally under the action of ahigh-temperature/high-pressure steam produced by the heat-recovery typesteam generation boiler and an electric generator operatively coupled toa rotor shaft of the steam turbine for generating electric energy, beingdriven through rotation of the rotor shaft. The condenser mentionedabove serves for condensing to water (condensed water) the steamdischarged from the steam turbine of the steam turbine power generationequipment. In the combined power plant described above, the condensedwater is used in the evaporator of the refrigeration system and therefrigerant vapor generated by the evaporator is pressurized by therefrigerant compressor. Heat carried by the pressurized refrigerantvapor is utilized for heating feed water of the heat-recovery type steamgeneration boiler utilized for recovery by the steam turbine as power.

[0022] In a preferred mode for carrying out the invention in conjunctionwith the combined power plant described above, the evaporator of therefrigeration system may be disposed within the intake-air coolingchamber of the intake-air cooling type gas turbine power equipment forcooling the intake air, and the refrigerant vapor leaving the evaporatormay be compressed by the refrigerant compressor to thereby betransformed to a pressurized refrigerant vapor.

[0023] According to yet another aspect of the invention, there isprovided a combined power plant, which includes intake-air cooling typegas turbine power equipment, a heat-recovery type steam generationboiler, steam turbine power generation equipment and a condenser. In thecombined power plant, the intake-air cooling type gas turbine powerequipment includes a refrigeration system comprised of an evaporator anda refrigerant compressor, an intake-air cooling chamber for cooling airtaken in from the atmosphere by the evaporator of the refrigerationsystem, an air compressor for compressing the air cooled by theintake-air cooling chamber to thereby produce compressed air, acombustor for burning a fuel supplied from an external system with thecompressed air produced by said air compressor to thereby produce acombustion gas, a gas turbine driven rotationally under the action ofthe combustion gas produced by the combustor, and an electric generatoroperatively coupled to a rotor shaft of the gas turbine for generatingelectric energy, being driven through rotation of the rotor shaft. Theheat-recovery type steam generation boiler mentioned above serves forrecovering a quantity of heat carried by the combustion exhaust gasdischarged from the gas turbine of the gas turbine power equipment. Onthe other hand, the steam turbine power generation equipment mentionedabove includes a steam turbine driven rotationally under the action of ahigh-temperature/high-pressure steam produced by the heat-recovery typesteam generation boiler and an electric generator operatively coupled toa rotor shaft of the steam turbine for generating electric energy, beingdriven through rotation of the rotor shaft. The condenser mentionedabove serves for condensing to water (condensed water) the steamdischarged from the steam turbine of the steam turbine power generationequipment. In the combined power plant described above, refrigerantvapor discharged from the evaporator of the refrigeration system ispressurized to a pressurized refrigerant vapor by the refrigerantcompressor, the pressurized refrigerant vapor being fed to the condenserof the refrigeration system where the pressurized refrigerant vaporundergoes heat exchange with the condensed water produced by thecondenser to thereby heat the condensed water while the pressurizedrefrigerant vapor itself is condensed to a refrigerant liquid(liquid-phase refrigerant) to be fed back to the evaporator, whereas thecondensed water as heated is fed to the heat-recovery type steamgeneration boiler.

[0024] In a further preferred mode for carrying out the invention inconjunction with the combined power plant described just above, theevaporator of the refrigeration system may be disposed within theintake-air cooling chamber of the intake-air cooling type gas turbinepower equipment for cooling the intake air, and the refrigerant vaporleaving the evaporator may be compressed by the refrigerant compressorto thereby be transformed to the pressurized refrigerant vapor.

[0025] As mentioned previously, in the conventional intake-air coolingtype gas turbine power equipment as well as the conventional combinedpower plant in which the intake-air cooling type gas turbine powerequipment is employed, the heat recovered by the evaporator upon coolingof the intake air and the heat generated in the course of operation ofthe refrigerant compressor in the refrigeration system are dissipated tothe atmosphere from the cooling tower and/or other cooling apparatus,involving the heat loss. By contrast, in the intake-air cooling type gasturbine power equipment and the combined power plant employing the sameaccording to the present invention, the heat mentioned above can beutilized as a heat source for reheating the intake air for the gasturbine intake air and/or as heat source for producing steam and forheating feed water for an external electric power generation systemand/or can be recovered for utilization in an external heat utilizationsystem such as thermal processes, energy service center or the like.Thus, occurrence of heat loss can be suppressed to a possible minimum.

[0026] At this juncture, description will be made of the refrigerationsystem employed according to the present invention. Assuming thatwater/steam is to be used as the refrigerant, heat substantiallyequivalent to heat of vaporization of water is deprived of from theambient or a heat transfer medium upon expansion of water under highvacuum e.g. of 6.5 mmHg, whereby the ambient temperature is lowered orthe heat transfer medium is cooled. The refrigerant water itselftransforms into steam (gas) which undergoes compression work to therebybe compressed and resumes the phase of water through condensation. Theliquid-phase water or condensed water is again expanded under highvacuum. In this manner, a Rankine cycle or so-called heat pump in whichexpansion/compression/condensation process is repeated is carried out,which provides the fundamental basis for the refrigeration.

[0027] By using the refrigeration system for cooling the intake air ofthe gas turbine, the intake air temperature of e.g. 30 C. can be loweredto a level within a range of 10 C. to 15 C. When the temperature of theintake air of the gas turbine is lowered, the mass flow of the intakeair to be consumed in the combustion with the fuel and to be used forcooling the high-temperature components will necessarily increase. Thus,the output of the gas turbine can be increased, while cooling of thehigh-temperature components can be realized with enhanced efficiency.

[0028] In addition to the refrigeration system where the water/steam isused as the refrigerant, there exists refrigeration systems in whichdedicated refrigerant such as substitute freon, ammonia or the like isemployed. Further, for driving the refrigerant compressor of therefrigeration system, there may be adopted electric motor drive, gas orsteam turbine drive, engine drive by diesel engine or gasoline engine,single-shaft type combined cycle drive or the like. The refrigerationsystem may be realized by a given one of various combinations of therefrigerating machines, refrigerants and the drives mentioned above.

[0029] The above and other objects, features and attendant advantages ofthe present invention will more easily be understood by reading thefollowing description of the preferred embodiments thereof taken, onlyby way of example, in conjunction with the accompanying drawings

BRIEF DESCRIPTION OF THE DRAWINGS

[0030] In the course of the description which follows, reference is madeto the drawings, in which:

[0031]FIG. 1A is a block diagram showing a system configuration of anintake-air cooling type gas turbine power plant according to a firstembodiment of the present invention;

[0032]FIG. 1B is a block diagram showing a modification of theintake-air cooling type gas turbine power plant shown in FIG. 1A;

[0033]FIG. 2 is a block diagram showing a system configuration ofintake-air cooling type gas turbine power equipment according to asecond embodiment of the present invention;

[0034]FIG. 3 is a block diagram showing a system configuration ofintake-air cooling type gas turbine power equipment according to a thirdembodiment of the present invention;

[0035]FIG. 4 is a block diagram showing a system configuration ofintake-air cooling type gas turbine power equipment according to afourth embodiment of the present invention;

[0036]FIG. 5 is a block diagram showing a system configuration of acombined power plant according to a fifth embodiment of the presentinvention;

[0037]FIG. 6 is a block diagram showing a system configuration of acombined power plant according to a sixth embodiment of the presentinvention;

[0038]FIG. 7 is a block diagram showing a system configuration of acombined power plant according to a seventh embodiment of the presentinvention;

[0039]FIG. 8 is a block diagram showing a system configuration of acombined power plant according to an eighth embodiment of the presentinvention;

[0040]FIG. 9 is a block diagram showing a system configuration of acombined power plant according to a ninth embodiment of the presentinvention;

[0041]FIG. 10 is a block diagram showing a system configuration of acombined power plant according to a tenth embodiment of the presentinvention;

[0042]FIG. 11 is a block diagram showing a system configuration of acombined power plant according to an eleventh embodiment of the presentinvention;

[0043]FIG. 12 is a block diagram showing a system configuration of acombined power plant according to a twelfth embodiment of the presentinvention;

[0044]FIG. 13 is a block diagram showing a system configuration of acombined power plant according to a thirteenth embodiment of the presentinvention;

[0045]FIG. 14 is a block diagram showing a system configuration of acombined power plant according to a fourteenth embodiment of the presentinvention;

[0046]FIG. 15 is a block diagram showing a system configuration of anintake-air cooling refrigeration system employed in a conventional gasturbine power plant;

[0047]FIG. 16 is a block diagram showing a system configuration of aconventional intake-air cooling type gas turbine power equipment; and

[0048]FIG. 17 is a block diagram showing a system configuration of aconventional combined power plant.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0049] The present invention will be described in detail in conjunctionwith what is presently considered as preferred or typical embodimentsthereof by reference to the drawings. In the following description, likereference characters designate like or corresponding parts throughoutthe several views.

[0050] As mentioned previously, in the conventional intake-air coolingtype gas turbine power equipment as well as in the conventional combinedpower plant employing the same, the heat (Q1) generated upon driving ofthe refrigerant compressor and the heat (Q2) deprived of the intake airof the gas turbine intake air upon cooling thereof with watercirculating through the suction-air cooling chamber and the evaporatorare dissipated from the cooling tower and/or other additional coolingapparatus by way of heat transfer medium (water) discharged from thecondenser of the refrigeration system employed for cooling the intakeair of the gas turbine. By contrast, in the intake-air cooling type gasturbine power equipment and the combined power plant employing the sameaccording to the present invention, the heat (Q1; Q2) mentioned above iscarried by the compressed refrigerant vapor discharged from therefrigerant compressor and supplied to an external heat utilizationsystem or systems to be recovered for utilization therein. Thus, heatloss of the intake-air cooling type gas turbine power equipment or thecombined power equipment as a whole can be suppressed effectively, whichin turn means that the performance or operation efficiency of theintake-air cooling type gas turbine power equipment as well as that ofthe combined power equipment can be significantly enhanced when comparedwith the conventional equipment and plant.

Embodiment 1

[0051]FIG. 1A is a block diagram showing a system configuration ofintake-air cooling type gas turbine power equipment according to a firstembodiment of the present invention. In the intake-air cooling type gasturbine power equipment now under consideration, a refrigeration systemis employed in which water/steam is employed as a refrigerant.

[0052] Referring to FIG. 1A, a refrigerant compressor 02 is driven by anelectric motor 01 to compress a steam serving as a refrigerant. Thepressurized steam discharged from the refrigerant compressor 02 at anincreased pressure is supplied to a heat utilization system 80 in whichheat carried by the pressurized steam is recovered to be utilized. As aresult of this, the steam is condensed to water (condensed water), whichis then circulated as a refrigerant liquid to an evaporator 05 disposedwithin an intake-air cooling chamber 10. In the evaporator 05 whoseinterior is maintained at a high vacuum level, the water undergoesexpansion to be transformed to the steam. Upon transformation to thesteam, water deprives heat equivalent or corresponding to the latentheat of vaporization to thereby refrigerate the ambient atmosphere. Onthe other hand, intake air 07 is supplied to the intake-air coolingchamber 10 as the feed air 09 after purification/noise reduction in asuction chamber 08. The air fed to the intake-air cooling chamber 10 isrefrigerated under cooling action of the evaporator 05 disposed withinthe intake-air cooling chamber 10 to be delivered therefrom as cooledair 11. The cooled air 11 is subsequently supplied to an air compressor12 to be compressed and discharged as compressed air 13 which is thenfed to a combustor 15. In the combustor 15, the compressed air 13undergoes combustion with fuel 14 charged from a relevant system (notshown), as a result of which a high-temperature combustion gas 16 isproduced and fed to a gas turbine 17. Under the action of thehigh-temperature combustion gas, the gas turbine 17 is drivenrotationally, whereby an electric generator 18 operatively coupled to arotor shaft of the gas turbine is driven through rotation of the rotorshaft, whereby electric energy is generated.

[0053] In the intake-air cooling type gas turbine power equipmentaccording to the first embodiment of the invention, the water/steamserving as the refrigerant for the refrigerating machine is caused tocirculate through or between the heat utilization system 80 installedexternally and the evaporator 05 of the refrigerating machine, whereinthe pressurized steam discharged from the refrigerant compressor carriesthe heat generated upon compression of the refrigerant vapor produced bythe refrigerant compressor as well as the heat transferred from the gasturbine intake air (air) upon cooling thereof is straightforwardly fedto the heat utilization system to be recovered for utilization as theheat carried by the pressurized steam after compression by therefrigerant compressor 02. Thus, with the arrangement of the intake-aircooling type gas turbine power equipment according to the instantembodiment of the invention, significantly high heat recovery efficiencycan be achieved.

[0054] More specifically, in the intake-air cooling type gas turbinepower equipment now under consideration, the evaporator 05 whichconstitutes a part of the refrigeration system is disposed within theintake-air cooling chamber 10 with a view to recovering directly theheat carried by the gas turbine intake air. By virtue of the arrangementin which the evaporator 05 of the refrigeration system is disposeddirectly within the intake-air cooling chamber 10 as mentioned above,not only the heat recovery efficiency for the gas turbine intake air canbe increased but also the intake-air cooling type gas turbine powerequipment can be designed and realized in a compact structure in whichthe refrigeration system and the intake-air cooling chamber are combinedwith each other as described above.

[0055]FIG. 1B is a block diagram showing a modification of theintake-air cooling type gas turbine power equipment shown in FIG. 1A.Referring to FIG. 1B, the evaporator 05 is disposed externally of theintake-air cooling chamber 10, wherein cold water serving as a heattransfer medium is caused to circulate through the evaporator 05 and theintake-air cooling chamber 10 for thereby recovering the heat carried bythe gas turbine intake air in an indirect manner. In the case of themodified plant shown in FIG. 1B, the heat recovery efficiency maycertainly be degraded more or less. However, because the refrigerationsystem can be used for cooling not only the gas turbine intake air butalso other equipment or components which are disposed adjacently andrequire cooling, the cost involved in the installation as well asoperation can be reduced. Of course, whether the evaporator 05 is to beinstalled internally or externally of the intake-air cooling chamber 10can be selectively decided at the stage of plant design in considerationof advantages brought about by the installation of the evaporatorinternally or externally of the intake-air cooling chamber. The sameholds true in succeeding embodiments.

Embodiment 2

[0056]FIG. 2 is a block diagram showing a system configuration ofintake-air cooling type gas turbine power equipment according to asecond embodiment of the present invention. Also in the intake-aircooling type gas turbine power equipment now of concern, a refrigerationsystem is adopted in which water/steam is employed as the refrigerant.Referring to FIG. 2, reference numeral 50 denotes a heater disposedwithin the intake-air cooling chamber 10 at a location near to the exitside of the cooled air discharged from the intake-air cooling chamber10. In the intake-air cooling type gas turbine power equipment accordingto the instant embodiment of the invention, a part of the pressurizedsteam discharged from the refrigerant compressor 02 constituting a partof the refrigeration system is fed directly to the heat utilizationsystem 80, whereas the other part of the pressurized steam is suppliedindirectly to the heat utilization system 80 after flowing through theheater 50. Except for the arrangement mentioned just above, theintake-air cooling type gas turbine power equipment according to thesecond embodiment of the invention is identical with that shown in FIG.1A.

[0057] Referring to FIG. 1B, the refrigerant compressor 02 is driven bythe electric motor 01 to compress a steam serving as a refrigerant. Apart of the pressurized steam discharged from the refrigerant compressor02 at an increased pressure is supplied to the heat utilization system80 in which heat carried by the pressurized steam is recovered to beutilized. The other or remaining part of the pressurized steam isutilized as heat source for the heater 50 and then supplied to the heatutilization system to be recovered for utilization. The feed air 09 isintroduced into the intake-air cooling chamber 10 to be cooled undercooling action of the evaporator 05 disposed within the intake-aircooling chamber. Subsequently, the feed air 09 is heated and dried tosome extent in the heater 50 and then supplied to the air compressor 12as the cooled air 11. Operations of the other components are same asthose of corresponding ones in the intake-air cooling type gas turbinepower equipment according to the first embodiment of the invention.

[0058] In the intake-air cooling type gas turbine power equipmentaccording to the second embodiment of the invention, a part of thewater/steam serving as the refrigerant is supplied to the heatutilization system installed externally of the power equipment to berecovered for utilization, while the remaining part of the water/steamis first made of as the heat source for the heater disposed within theintake-air cooling chamber and then supplied to the heat utilizationsystem installed externally, circulating thus through the heatutilization system and the refrigeration system. By virtue of thearrangement mentioned just above, the pressurized steam discharged fromthe refrigerant compressor carries both the heat transferred from thegas turbine intake air (air) upon cooling thereof and the heattransferred upon compression of the refrigerant steam by the refrigerantcompressor, wherein the heat carried by the pressurized steam isutilized as the heat source for the heater 50 disposed within theintake-air cooling chamber and at the same time recovered forutilization in the heat utilization system 80 installed externally ofthe intake-air cooling type gas turbine power equipment. Thus, enhancedheat recovery efficiency can be achieved.

Embodiment 3

[0059]FIG. 3 is a block diagram showing a system configuration ofintake-air cooling type gas turbine power equipment according to a thirdembodiment of the present invention. A refrigeration system is adoptedin which dedicated refrigerant such as substitute freon, ammonia or thelike is employed as the refrigerant. In FIG. 3, reference numeral 03denotes a condenser constituting a part of the refrigeration system. Therefrigerant circulates through a closed loop constituted by therefrigerant compressor 02, the condenser 03 and the evaporator 05. Acircuit for circulating a heat carrying medium (e.g. water) is providedbetween the condenser 03 and the heat utilization system 80. Except forthe arrangement described just above, the intake-air cooling type gasturbine power equipment according to the third embodiment is essentiallysame as the equipment shown in FIG. 1A.

[0060] Referring to FIG. 3, the refrigerant is compressed by therefrigerant compressor 02 driven by the electric motor 01. Thepressurized refrigerant vapor discharged from the refrigerant compressor02 at an increased pressure is then supplied to the condenser 03. Withinthe condenser 03, the pressurized refrigerant vapor undergoes heatexchange with the heat transfer medium or heating medium (e.g. water)which is circulated through the condenser and the heat utilizationsystem 80 installed externally, as a result of which the refrigerantvapor of high pressure is cooled to change or transform the phase to aliquid refrigerant phase. On the other hand, the heat transfer mediumhaving the temperature increased by the heat carried by the refrigerantof high pressure through the heat exchange is supplied to the heatutilization system 80 where the heat carried by the heat transfer mediumis recovered for utilization. The refrigerant having changed the phaseto liquid in the condenser 03 undergoes expansion within the evaporator05, which results in that the liquid refrigerant changes to the gasphase. In that case, the ambient atmosphere is deprived of heatequivalent to the latent heat of vaporization, whereby the ambient feedair 09 is cooled. The gas refrigerant discharged from the evaporator 05is again compressed by the refrigerant compressor 02 to be transformedto pressurized refrigerant vapor. Through the processes mentioned above,a refrigeration system cycle is realized. In other words, in therefrigeration system according to the third embodiment of the invention,the refrigerant such as substitute freon or the like circulates throughthe refrigeration system cycle, wherein circulation with the externalsystem is realized indirectly through the medium of the heat transfermedium (e.g. water) which circulates between the condenser 03 and theheat utilization system 80.

[0061] The feed air 09 is introduced into the intake-air cooling chamber10 to be cooled under the cooling action of the evaporator 05 disposedwithin the intake-air cooling chamber 10. Subsequently, the feed air 09is supplied to the air compressor 12 as the cooled air 11. Succeedingoperations of the intake-air cooling type gas turbine power equipmentaccording to the instant embodiment is essentially same as the equipmentaccording to the first embodiment of the invention.

[0062] As is apparent from the above description, in the intake-aircooling type gas turbine power equipment according to the thirdembodiment of the invention, the circulation of the refrigerant isconfined only within the intake-air cooling type gas turbine powerequipment, wherein circulation between the intake-air cooling type gasturbine power equipment and the external system is realized bycirculating water serving as the heat transfer medium through the formerand the latter. In other words, supply of the heat carried by thepressurized refrigerant vapor to the heat utilization system installedexternally is realized through intervention of the heat transfer medium.Thus, when compared with the intake-air cooling type gas turbine powerequipment according to the first embodiment of the invention, heat lossmay occur to some extent upon heat exchange with the heat transfermedium. However, because both the heat generated upon compression of therefrigerant by the refrigerant compressor 02 and the heat received fromthe ambient upon cooling of the feed air 09 are carried by thecompressed refrigerant vapor of high pressured discharged from therefrigerant compressor and supplied to the heat utilization systeminstalled externally through the medium of water serving as the heattransfer medium, effective heat recovery and utilization can beachieved.

Embodiment 4

[0063]FIG. 4 is a block diagram showing a system configuration ofintake-air cooling type gas turbine power equipment according to afourth embodiment of the present invention. In the refrigeration systemas adopted, substitute freon, ammonia or the like is employed as therefrigerant. In FIG. 4, reference numeral 50 denotes a heater installedwithin the suction-air cooling chamber 10 at the cooled-air exit sidethereof. The intake-air cooling type gas turbine power equipmentaccording to the fourth embodiment of the invention differs from that ofthe third embodiment in that the pressurized refrigerant vapor flowingfrom the refrigerant compressor 02 to the condenser 03 in the intake-aircooling type gas turbine power equipment of the third embodiment iscaused to flow through the heater 50 installed within the intake-aircooling chamber on the way. Except for this difference, the intake-aircooling type gas turbine power equipment according to the instantembodiment of the invention is essentially same as that of the thirdembodiment.

[0064] Referring to FIG. 4, the refrigerant is compressed by therefrigerant compressor 02 driven by the electric motor 01. Thepressurized refrigerant vapor discharged from the refrigerant compressor02 at an increased pressure is fed to the heater 50, wherein thepressurized refrigerant vapor is utilized as a heat source for heatingthe intake air before being supplied to the condenser 03. Within thecondenser 03, the pressurized refrigerant vapor undergoes heat exchangewith the heat transfer medium which is circulated between the condenser03 and the heat utilization system 80 installed externally, as a resultof which the pressurized refrigerant vapor is cooled to change the phaseto a liquid refrigerant phase. On the other hand, the water or heattransfer medium having the temperature increased by the heat carried bythe pressurized refrigerant vapor through the heat exchange is suppliedto the heat utilization system 80 where the heat carried by the water orheat transfer medium is recovered for utilization. The refrigeranthaving changed into the liquid phase in the condenser 03 undergoesexpansion within the evaporator 05, which results in that the liquidrefrigerant changes to a gas phase. In that case, the ambient atmosphereis deprived of heat equivalent to the latent heat of vaporization,whereby the feed air 09 is cooled. The gas refrigerant discharged fromthe evaporator 05 is again compressed by the refrigerant compressor 02to be transformed to pressurized refrigerant vapor. Through theprocesses mentioned above, a refrigeration system cycle is realized. Inother words, in the refrigeration system of the equipment according tothe instant embodiment of the invention, the refrigerant such assubstitute freon or the like circulates through the refrigeration systemcycle, wherein circulation between the intake-air cooling type gasturbine power equipment and the external system is realized indirectlythrough the medium of the heat transfer medium (e.g. water) whichcirculates through the condenser 03 and the heat utilization system 80.

[0065] The feed air 09 is introduced into the intake-air cooling chamber10 to be cooled under the cooling action of the evaporator 05 disposedwithin the intake-air cooling chamber 10. Subsequently, the feed air 09is heated and dried to some extent in the heater 50 and then supplied tothe air compressor 12 as the cooled air 11. Operations of the othercomponents are same as corresponding ones in the intake-air cooling typegas turbine power equipment according to the other embodiments of theinvention described hereinbefore.

[0066] As is apparent from the above description, in the intake-aircooling type gas turbine power equipment according to the fourthembodiment of the invention, circulation of the refrigerant is confinedonly within the intake-air cooling type gas turbine power equipment,wherein the circulation between the intake-air cooling type gas turbinepower equipment and the external system is realized by circulating waterserving as the heat transfer medium through the former and the latter.In other words, supply of the heat carried by the pressurizedrefrigerant vapor to the heat utilization system installed externally isrealized through intervention of the heat transfer medium. Thus, whencompared with the intake-air cooling type gas turbine power equipmentaccording to the third embodiment of the invention, heat loss may occurto some extent upon heat exchange with the heat transfer medium.However, because the heat generated upon compression of the refrigerantby the refrigerant compressor 02 as well as the heat received from theintake air of the gas turbine upon cooling thereof are carried by thecompressed refrigerant vapor of high pressured discharged from therefrigerant compressor and supplied to the heat utilization systeminstalled externally, effective heat recovery and utilization can beachieved.

Embodiment 5

[0067]FIG. 5 is a block diagram showing a system configuration of acombined power plant according to a fifth embodiment of the presentinvention. The combined power plant is comprised of a heat-recovery typesteam generation boiler and steam turbine power generation equipmentwhich are operatively connected to or combined with intake-air coolingtype gas turbine power equipment, in which a refrigeration system isadopted where water/steam is employed as the refrigerant. Referring toFIG. 5, reference numeral 20 denotes a heat-recovery type steamgeneration boiler to which an exhaust gas 19 of the gas turbine 17 isintroduced to recover heat therefrom, 21 designateshigh-temperature/high-pressure steam extracted from the heat-recoverytype steam generation boiler, 22 denotes a steam turbine drivenrotationally under the action of the high-temperature/high-pressuresteam, 23 denotes an electric generator operatively coupled to a shaftof the steam turbine 22, numeral 24 designates exhaust steam dischargedfrom the steam turbine, 25 denotes a condenser for condensing theexhaust steam to water, 26 designates condensed water discharged fromthe condenser to be fed back to the heat-recovery type steam generationboiler 20, and numeral 27 designates exhaust gas discharged after havingpassed through the heat-recovery type steam generation boiler.

[0068] A part of the pressurized steam discharged from the refrigerantcompressor 02 of the refrigeration system is branched or tapped on theway of flowing to the heat-recovery type steam generation boiler 20 tobe charged into a steam pipe extending from the heat-recovery type steamgeneration boiler 20 at an intermediate portion thereof. Another part ofthe pressurized steam discharged from the refrigerant compressor 02 isfed to a pipe which leads to a low-pressure section of the steam turbine22 to be used as the steam of lower pressure than thehigh-temperature/high-pressure steam 21 extracted from the heat-recoverytype steam generation boiler. On the other hand, a part of the condensedwater is fed back to the heat-recovery type steam generation boiler 20,while the other part thereof is fed back to the evaporator 05 of therefrigeration system.

[0069] With the arrangement described above, heat energy of thepressurized steam discharged from the refrigerant compressor 02 can beinjected to the steam turbine 22 directly and/or by way of theheat-recovery type steam generation boiler 20 to be utilized as a partof energy for driving the electric generator 23 operatively coupled tothe steam turbine. In this manner, effective utilization of heat can beachieved. The exhaust steam of the steam turbine 22 is condensed towater in the condenser 25, a part of the condensed water being fed backto the evaporator 05. The condensed water is utilized for cooling theintake air in the evaporator 05 and vaporized to steam which is then fedback to the refrigerant compressor 02. In this way, heat of thepressurized steam of the refrigeration system can be effectivelyutilized.

Embodiment 6

[0070]FIG. 6 is a block diagram showing a system configuration of acombined power plant according to a sixth embodiment of the presentinvention. The combined power plant is comprised of a heat-recovery typesteam generation boiler and a heat utilization system which areoperatively connected to or combined with the intake-air cooling typegas turbine power equipment, and additionally includes a thermal processother than the above-mentioned heat utilization system. A refrigerationsystem is adopted where water/steam is employed as the refrigerant.Referring to FIG. 6, reference numeral 20 denotes an heat-recovery typesteam generation boiler to which an exhaust gas 19 of the gas turbine 17is introduced to recover heat therefrom, 80 denotes a heat utilizationsystem connected to the boiler mentioned just above, and numeral 21designates high-temperature/high-pressure steam extracted from theheat-recovery type steam generation boiler to be supplied to the heatutilization system. Further, reference numeral 81 denotes a thermalprocess other than the heat utilization system 80.

[0071] In the combined power plant shown in FIG. 6, thehigh-temperature/high-pressure steam 21 and water resulting from thephase conversion of the high-temperature/high-pressure steam 21 deprivedof heat in the heat utilization system 80 circulates between theheat-recovery type steam generation boiler 20 and the heat utilizationsystem 80. The thermal process 81 is not connected to the heat-recoverytype steam generation boiler 20. The pressurized steam discharged fromthe refrigerant compressor 02 is branched on the way of flowing, wherebya part of the pressurized steam is caused to merge into the flow of thehigh-temperature/high-pressure steam 21 to be supplied to the heatutilization system 80. Thus, heat carried by thehigh-temperature/high-pressure steam 21 is utilized in the heatutilization system 80. The other part of thehigh-temperature/high-pressure steam 21 is supplied to the other thermalprocess 81 for utilization of the heat carried by the steam. The steamsupplied to the heat utilization system 80 is converted to water, a partof which is fed back to the evaporator 05 of the refrigeration systemtogether with water resulting from condensation of the steam deprived ofheat through the thermal process 81. In this way, effective utilizationof heat of the pressurized steam discharged from the refrigerantcompressor 02 of the refrigeration system can be accomplished.

Embodiment 7

[0072]FIG. 7 is a block diagram showing a system configuration of acombined power plant according to a seventh embodiment of the presentinvention. The combined power plant is comprised of an heat-recoverytype steam generation boiler, steam turbine power generation equipmentand a heat utilization system which are operatively connected to theintake-air cooling type gas turbine power equipment. In this combinedpower plant, a refrigeration system is adopted where water/steam isemployed as the refrigerant. Referring to FIG. 7, reference numeral 20denotes an heat-recovery type steam generation boiler to which anexhaust gas 19 of the gas turbine 17 is introduced to recover heattherefrom, 22 denotes a steam turbine, 23 denotes an electric generatorconnected to the steam turbine, and 25 denotes a condenser. The steamturbine power generation equipment is constituted by the componentsmentioned just above. Incidentally, the heat utilization system isdenoted by reference numeral 80. The steam turbine power generationequipment and the heat utilization system 80 are connected in parallelrelative to the heat-recovery type steam generation boiler 20. Thepressurized steam discharged from the refrigerant compressor 02 of therefrigeration system is supplied to the destined heat utilization system80 where heat carried by the pressurized steam is utilized effectively.Thus, in the destined heat utilization system 80, the pressurized steamis converted into water which is mixed with water discharged from thecondenser 25. Apart of water is fed back to the heat-recovery type steamgeneration boiler 20 with the other part of water being fed back to theevaporator 05 of the refrigeration system. In this way, there can beachieved effective utilization of heat of the pressurized steamdischarged from the refrigerant compressor.

Embodiment 8

[0073]FIG. 8 is a block diagram showing a system configuration of acombined power plant according to an eighth embodiment of the presentinvention. In the combined power plant now under consideration, aheat-recovery type steam generation boiler and steam turbine powergeneration equipment connected to the boiler are operatively connectedto intake-air cooling type gas turbine power equipment. In this plant, arefrigeration system is adopted in which dedicated refrigerant such assubstitute freon or ammonia is employed as the refrigerant. Referring tothe figure, the refrigeration system includes a condenser 03. Referencenumeral 20 denotes the heat-recovery type steam generation boiler towhich the exhaust gas 19 of the gas turbine 17 is introduced to recoverheat therefrom. Reference numeral 21 designateshigh-temperature/high-pressure steam discharged from thehigh-temperature/high-pressure steam, 22 denotes a steam turbine, 23denotes an electric generator, 25 denotes a condenser, and 26 denotes acondensed water.

[0074] With an arrangement of the combined power plant according to theinstant embodiment of the invention, a part of the condensed water 26fed back to the heat-recovery type steam generation boiler 20 from thecondenser 25 of the steam turbine power generation equipment iscirculated to the condenser 03 of the refrigeration system. Thus, heatavailable in the refrigeration system can be utilized for heating thecondensed water. Thus, effective utilization of heat can be realized.

Embodiment 9

[0075]FIG. 9 is a block diagram showing a system configuration of acombined power plant according to a ninth embodiment of the presentinvention. In the combined power plant now of concern, the intake-aircooling type gas turbine power equipment is operatively combined with aheat-recovery type steam generation boiler and steam turbine powergeneration equipment which is connected to that boiler. Furthermore, aheat utilization system is provided independent of the heat-recoverytype steam generation boiler and the steam turbine power generationequipment. A refrigeration system is adopted in which dedicatedrefrigerant such as substitute freon or ammonia is employed as therefrigerant. As can be seen in FIG. 9, a refrigeration system includes acondenser 03. The heat utilization system is denoted by referencenumeral 80.

[0076] With the above arrangement of the combined power plant accordingto the ninth embodiment of the invention, a water circulation path isprovided between the condenser 03 of the steam turbine power generationequipment and the heat utilization system 80 for realizing effectiveutilization of exhaust heat of the condenser 03 in the heat utilizationsystem 80.

Embodiment 10

[0077]FIG. 10 is a block diagram showing a system configuration of acombined power plant according to a tenth embodiment of the presentinvention. The combined power plant is comprised of intake-air coolingtype gas turbine power equipment, an heat-recovery type steam generationboiler, steam turbine power generation equipment and a heat utilizationsystem, wherein the steam turbine power generation equipment and theheat utilization system are disposed in parallel to the boiler. Arefrigeration system is adopted in which dedicated refrigerant such assubstitute freon or ammonia is employed as the refrigerant. As can beseen in FIG. 10, a condenser 03 is provided in a refrigeration system.Reference numeral 80 denotes the heat utilization system.

[0078] With the above arrangement of the combined power plant accordingto the tenth embodiment of the invention, a water circulation path isprovided between the condenser 03 of the refrigeration system and theheat utilization system 80 for realizing effective utilization of theexhaust heat of the condenser 03 in the heat utilization system 80.

Embodiment 11

[0079]FIG. 11 is a block diagram showing a system configuration of acombined power plant according to an eleventh embodiment of the presentinvention. The concept underlying the combined power plant now underconsideration corresponds to combination of the concepts incarnated inthe second and fifth embodiments of the invention described hereinbeforeby reference to FIGS. 2 and 5. In the combined power plant according tothe eleventh embodiment of the invention, a refrigeration system inwhich water/steam is employed as the refrigerant is adopted as theintake-air cooling system. Referring to FIG. 11, intake air andcombustion gas resulting from combustion thereof flows along a pathextending along a suction chamber 08, an intake-air cooling chamber 10,an air compressor 12, a combustor 15, a gas turbine 17 and anheat-recovery type steam generation boiler 20.

[0080] An electric generator 18 is operatively coupled to a rotatableshaft common to both the air compressor 12 and the gas turbine 17.Disposed within the intake-air cooling chamber 10 is an evaporator 05, adehumidifier 40 and a heater 50. The refrigeration system is composed ofa refrigerant compressor 02, an electric motor 01 and an evaporator 05which is disposed within the intake-air cooling chamber 10. Operativelycoupled to the heat-recovery type steam generation boiler 20 is steamturbine power generation equipment which is comprised of a steam turbine22, an electric generator 23 and a condenser 25. For driving the steamturbine power generation equipment, high-temperature/high-pressure steam21 is supplied from the heat-recovery type steam generation boiler 20.In addition to the electric power generation system described above, aheat utilization system 80 is provided. In FIG. 11, broken linesrepresent steam flow paths, solid lines represent liquid flow paths, andsingle-dotted broken lines represent information/signal paths.

[0081] The steam discharged from the evaporator 05 disposed within theintake-air cooling chamber is compressed by the refrigerant compressor02 driven by the electric motor 01 and discharged therefrom aspressurized steam. A part of this pressurized steam is caused to flowthrough the heater 50. Thereafter, the pressurized steam heated by theheater 50 merges into the pressurized steam discharged directly from therefrigerant compressor 02. The pressurized steam resultant from themerge is admixed to intermediate-pressure steam 21′ extracted from anintermediate section of the heat-recovery type steam generation boiler20 to be subsequently supplied to an intermediate section of the steamturbine 22 and the heat utilization system 80. The steam discharged fromthe steam turbine 22 is condensed to water by the condenser 25. A partof condensed water discharged from the condenser 25 is fed back to theevaporator 05 by means of a pump P1 while the other part is fed back tothe heat-recovery type steam generation boiler 20 by means of a pump P2.A part of the steam supplied to the heat utilization system 80 iscondensed and discharged in the liquid phase while the other part isdischarged in the gas phase, i.e., in the form of steam. A part of thecondensed water discharged from the heat utilization system 80 is led tothe exit side of the pump P1 to thereby be fed back to the heat-recoverytype steam generation boiler while the other part of water is led to theoutlet side of the pump P2 to be fed back to the evaporator 05. On theother hand, the steam discharged from the heat utilization system is ledto the inlet side of the refrigerant compressor 02. Paying attention toonly the refrigerating cycle, the intrinsic role of the refrigerantcompressor in the refrigerating cycle system is carried out by thecondenser 25. Thus, the system configuration can be simplified. In thecombined power plant according to the eleventh embodiment of theinvention, it has been assumed that the dehumidifier 40 is incorporated.However, installation of such dehumidifier is not always required. Inother words, decision as to whether the dehumidifier is to be installedor not may be left to discretion of the plant designer.

[0082] Furthermore, a valve 41 is installed in a pipe for supplyingwater to the evaporator 05 mounted within the intake-air cooling chamber10, while a valve 42 is installed in a feed pipe for feeding thepressurized steam to the heater 50. For controlling the opening degreesof these valves, a controller CPU is provided. In FIG. 11, referencesymbol X represents a desired power output value inputted to thecontroller CPU, X1 represents an actual power output of the gas turbinesystem, X2 represents an actual power output of the steam turbinesystem, D represents outlet temperature information of the suctionchamber 08, TX1 represents output of a temperature sensor incorporatedin the dehumidifier, A represents temperature information supplied tothe controller CPU from the temperature sensor of the dehumidifier, Brepresents a control signal supplied to the valve 41 from the controllerCPU, TX2 represents an output signal of a temperature sensor provided inassociation with the heater, A′ represents temperature information sentto the controller CPU from the temperature sensor of the heater, and B′represents a control signal supplied to the valve 42 from the controllerCPU.

[0083] When difference is found between the desired power output value Xof the gas turbine system and the actual power output X1 of the gasturbine system, the desired values to be detected by the temperaturesensors TX1 and TX2, respectively, are arithmetically determined by thecontroller CPU, whereon the controller CPU outputs the valve controlsignals B and B′ for canceling out the difference between thetemperature determined arithmetically and the actual temperature.

[0084] By contrast, when the desired power output value X indicates thecombined power output of the gas turbine system and the steam turbinesystem, the power output X2 of the steam turbine system is affected bythe factors such as the power output X1 of the gas turbine system, thetemperature information A′ outputted from a temperature sensor TX2 andthe like. Accordingly, characteristic relations among the power outputX2 of the steam turbine system, the power output X1 of the gas turbinesystem and the temperature information A′ outputted from the temperaturesensor TX2 installed at the outlet of the heater may be previouslystored in the controller CPU for allowing the controller CPU to issueproper or appropriate valve control command signals B and B′ for therebyregulate the outlet temperatures of the individual heaters. In thismanner, the intake-air cooling type gas turbine power equipment can beregulated by controlling the power output of the gas turbine system.

Embodiment 12

[0085]FIG. 12 is a block diagram showing a system configuration of acombined power plant according to a twelfth embodiment of the presentinvention. The concept underlying the combined power plant now underconsideration corresponds to a combination of the concepts incarnated,respectively, in the fourth and tenth embodiments described hereinbeforeby reference to FIGS. 4 and 10. In the combined power plant according tothe twelfth embodiment of the invention, a refrigeration system in whichsubstitute freon or ammonia is employed as the dedicated refrigerant isadopted as the intake-air cooling system. Referring to FIG. 12, the flowpath of the intake air and the combustion gas thereof extends along asuction chamber 08, an intake-air cooling chamber 10, an air compressor12, a combustor 15, a gas turbine 17 and an heat-recovery type steamgeneration boiler 20. An electric generator 18 is operatively coupled toa rotatable shaft common to both the air compressor 12 and the gasturbine 17. Disposed within the intake-air cooling chamber 10 are anevaporator 05, a dehumidifier 40 and a heater 50. These components arethe same as those in the plant according to the eleventh embodiment ofthe invention. Connected operatively to the evaporator 05 disposedwithin the intake-air cooling chamber 10 is a closed-loop refrigerationsystem which is constituted by a refrigerant compressor 02, an electricmotor 01 and a condenser 03. Besides, operatively coupled to theheat-recovery type steam generation boiler 20 is steam turbine powergeneration equipment which is comprised of a steam turbine 22, anelectric generator 23 and a condenser 25. In addition to the electricpower generation system described above, a destined heat utilizationsystem 80 is provided. In FIG. 12, broken lines represent steam flowpaths, while solid lines represent fluid flow paths.

[0086] The steam discharged from the steam turbine 22 is condensed towater in the condenser 25, a part of which is fed back to theheat-recovery type steam generation boiler 20 by means of the pump P1while the other part is fed to the condenser 03 by the pump P2 toundergo heat exchange with the refrigerant dedicated for the condenser03. A part of water whose temperature is increased by the condenser 03is fed back to the heat-recovery type steam generation boiler with theother part being supplied to the destined heat utilization system 80.Water having the temperature lowered in the heat utilization system isfed to the condenser 03 to be heated again.

[0087] At this juncture, it should be mentioned that the valves 41 and42 are controlled by the means similar to those described previously inconjunction with the eleventh embodiment although the controller CPU andinformation signal lines are not illustrated in FIG. 12. Further, eventhough the combined power plant according to the twelfth embodiment ofthe invention is shown as incorporating the dehumidifier 40, it is notalways necessary to install the dehumidifier. Whether the dehumidifieris to be installed or not may be left to discretion of the plantdesigner.

Embodiment 13

[0088]FIG. 13 is a block diagram showing a system configuration of acombined power plant according to a thirteenth embodiment of the presentinvention. The combined power plant now under consideration is sodesigned that the steam discharged from the refrigerant compressor 02 inthe combined power plant shown in FIG. 5 is condensed at the condenser25 together with the steam discharged from the steam turbine 22. In thecombined power plant according to the instant embodiment of theinvention, a refrigeration system in which water/steam is employed asthe refrigerant is adopted as the intake-air cooling system. Referringto FIG. 13, the flow path for the intake air and the combustion gasextends along a suction chamber 08, an intake-air cooling chamber 10, anair compressor 12, a combustor 15, a gas turbine 17 and a heat-recoverytype steam generation boiler 20. An electric generator 18 is operativelycoupled to a rotatable shaft common to both the air compressor 12 andthe gas turbine 17. Within the intake-air cooling chamber 10, only theevaporator 05 is disposed. Neither the dehumidifier nor a heater isprovided therein. The refrigerant compressor 02 and an electric motor 01are operatively coupled to the evaporator 05. On the other hand,operatively coupled to the heat-recovery type steam generation boiler 20is power generation equipment which is comprised of a steam turbine 22,an electric generator 23 and a condenser 25. In FIG. 13, broken linesrepresent steam flow paths, solid lines represent liquid flow paths, andsingle-dotted broken lines represent information/signal paths,respectively.

[0089] The pressurized steam discharged from the refrigerant compressor02 is caused to merge into the steam discharged from the steam turbine22 to be subsequently sent to the condenser 25. A part of waterdischarged from the condenser is fed back to the heat-recovery typesteam generation boiler 20 by means of the pump P1 while the other partis fed to the evaporator 05 of the intake-air cooling system by means ofthe pump P2. A valve 41 is installed in a pipe for feeding the water tothe evaporator 05. This valve 41 is controlled in accordance with avalve manipulation signal B which is arithmetically determined on thebasis of the desired output value X of the combined power plantcomprised of the gas turbine system and the steam turbine system, thegas turbine power output X1, the steam turbine power output X2, theoutlet temperature D of the suction chamber and the outlet temperature Aof the intake-air cooling chamber so that the output power whichconforms to the desired output value can be generated.

Embodiment 14

[0090]FIG. 14 is a block diagram showing a system configuration of acombined power plant according to a fourteenth embodiment of the presentinvention. In the combined power plant according to the instantembodiment, a refrigeration system in which water/steam is employed asthe refrigerant is adopted as the intake-air cooling system. Referringto FIG. 14, a flow path of the intake air and the combustion gasresulting from combustion thereof extend along a suction chamber 08, anintake-air cooling chamber 10, an air compressor 12, a combustor 15, agas turbine 17 and an heat-recovery type steam generation boiler 20. Anelectric generator 18 is operatively coupled to a rotatable shaft commonto both the air compressor 12 and the gas turbine 17. Disposed withinthe intake-air cooling chamber 10 is only an evaporator 05. Connectedoperatively to the evaporator 05 are the steam turbine power generationequipment which is comprised of a refrigerant compressor 02, a generatormotor 43 and a steam turbine 44. On the other hand, operatively coupledto the heat-recovery type steam generation boiler 20 is steam turbinepower generation equipment comprised of a steam turbine 22, an electricgenerator 23 and a condenser 25. In FIG. 14, broken lines representsteam flow paths, solid lines represent liquid flow paths, andsingle-dotted broken lines represent information/signal paths.

[0091] A part of the high-temperature/high-pressure steam 21 dischargedfrom the termination end of the steam path in the heat-recovery typesteam generation boiler 20 is supplied to the steam turbine 22 with theother part of the high-temperature/high-pressure steam 21 being suppliedto the steam turbine 44. The steam discharged from the evaporator 05installed within the intake-air cooling chamber is compressed by therefrigerant compressor 02. A part of the pressurized steam deliveredfrom the refrigerant compressor 02 is admixed with the steam extractedfrom an intermediate portion of the steam flow path in the heat-recoverytype steam generation boiler to be subsequently supplied to anintermediate section of the steam turbine 22. On the other hand, theother part of the steam is supplied to an intermediate section of thesteam turbine 44. The generator motor 43 is operated as the electricgenerator or the electric motor in dependence on the output of the steamturbine 44 and the load imposed to the refrigerant compressor 02. Inbrief, the generator motor 43 is operated in the electric generatingmode when electric energy can be taken out, while it is operated in themotor mode when the driving power is required. The steam discharged fromthe steam turbine 44 is caused to merge into the steam discharged fromthe steam turbine 22 to be subsequently sent to the condenser 25 wherethe steam is condensed to water. A part of the water is fed back to theheat-recovery type steam generation boiler 20 through the pump P1 withthe other part being fed to the evaporator 05 of the intake-air coolingchamber through the pump P2. A valve 41 is installed in a pipe forfeeding the water to the evaporator 05. This valve 41 is controlled inaccordance with a valve manipulation signal B which is arithmeticallydetermined on the basis of the desired output value X of the combinedpower plant comprised of the gas turbine system and the steam turbinesystem, the actual gas turbine power output X1, the actual steam turbinepower output X2, the outlet temperature D of the suction chamber and theoutlet temperature A of the intake-air cooling chamber so that theoutput power which conforms to the desired output value X can begenerated.

[0092] At this juncture, it should be mentioned that in the foregoingelucidation of the intake-air cooling type gas turbine power equipmentas well as the combined power plant including the intake-air coolingtype gas turbine power equipment according to the various embodiments ofthe invention, no description has been made concerning the cooling towerand other cooling apparatuses used for feeding coolant water to thecondenser and for cooling the coolant water having temperature raised bythe condenser as described hereinbefore in conjunction with theconventional refrigeration system. It should however be noted that inthe systems according to the present invention, such cooling tower orthe like cooling apparatuses of the conventional system may be employedin combination in case the cooling capacity required for cooling the gasturbine intake air exceeds the quantity of heat which is recovered forutilization in the heat utilization system.

[0093] Finally, it should be pointed out that although the presentinvention can be carried in six types of modes corresponding tocombinations of the embodiments shown in FIGS. 1 and 2 with those shownin FIGS. 5, 6 and 7 and six types of modes corresponding to theembodiments shown in FIGS. 8, 9 and 10, i.e., in twelve sorts of modesin total, the invention is never restricted to such modes.

[0094] Many modifications and variations of the present invention arepossible by various combinations of components or the like in the lightof the above techniques. It is therefore to be understood that withinthe scope of the appended claims, the invention may be practicedotherwise than as specifically described.

What is claimed is:
 1. Intake-air cooling type gas turbine powerequipment, comprising: a refrigeration system including an evaporatorand a refrigerant compressor, an intake-air cooling chamber for coolingair taken in from the atmosphere by said evaporator of saidrefrigeration system; an air compressor for compressing the air cooledin said intake-air cooling chamber to thereby produce compressed air; acombustor for burning a fuel supplied from an external system with thecompressed air produced by said air compressor to thereby produce acombustion gas; a gas turbine driven rotationally under the action ofsaid combustion gas produced by said combustor; and an electricgenerator operatively coupled to a rotor shaft of said gas turbine forgenerating electric energy, being driven through rotation of said rotorshaft, wherein the refrigerant vapor leaving said evaporator of saidrefrigeration system is compressed by means of said refrigerantcompressor to be transformed to a pressurized refrigerant vapor, andwherein heat carried by said pressurized refrigerant vapor is suppliedto a heat utilization system to be recovered for utilization. 2.Intake-air cooling type gas turbine power equipment according to claim 1, wherein said pressurized refrigerant vapor itself that leaves saidrefrigerant compressor is circulated through said heat utilizationsystem so that the heat carried by said pressurized refrigerant vaporcan be supplied to said heat utilization system for recovery. 3.Intake-air cooling type gas turbine power equipment according to claim 1, in which said refrigeration system further includes a condenser,wherein said pressurized refrigerant vapor leaving said refrigerantcompressor is fed to said condenser in which said pressurizedrefrigerant vapor undergoes heat exchange with a heat transfer mediumwhich circulates through said condenser and said heat utilizationsystem, and wherein heat carried by said compressed refrigerant vapor issupplied to said heat utilization system through the medium of said heattransfer medium to be recovered for utilization in said heat utilizationsystem.
 4. Intake-air cooling type gas turbine power equipment accordingto claims 1 to 3 , wherein a heater for heating and drying the aircooled by said intake-air cooling chamber is disposed within saidintake-air cooling chamber at a cooled-air outlet side thereof, andwherein heat carried by said pressurized refrigerant vapor leaving saidrefrigerant compressor is utilized as a source of heat for said heater.5. A combined power plant, comprising: intake-air cooling type gasturbine power equipment; a heat-recovery type steam generation boiler;steam turbine power generation equipment; and a condenser, saidintake-air cooling type gas turbine power equipment comprising: arefrigeration system including an evaporator and a refrigerantcompressor, an intake-air cooling chamber for cooling air taken in fromthe atmosphere by said evaporator of said refrigeration system; an aircompressor for compressing the air cooled in said intake-air coolingchamber to thereby produce compressed air; a combustor for burning afuel supplied from an external system with the compressed air producedby said air compressor to thereby produce a combustion gas; a gasturbine driven rotationally under the action of said combustion gasproduced by said combustor; and an electric generator operativelycoupled to a rotor shaft of said gas turbine for generating electricenergy, being driven through rotation of said rotor shaft, saidheat-recovery type steam generation boiler serving for recovering aquantity of heat carried by the combustion exhaust gas discharged fromsaid gas turbine of said gas turbine power equipment; said steam turbinepower generation equipment comprising: a steam turbine drivenrotationally under the action of a high-temperature/high-pressure steamproduced by said heat-recovery type steam generation boiler; and anelectric generator operatively coupled to a rotor shaft of said steamturbine for generating electric energy, being driven through rotation ofsaid rotor shaft; and said condenser serving for condensing to water thesteam discharged from said steam turbine of said steam turbine powergeneration equipment, wherein the condensed water is used in saidevaporator of said refrigeration system, refrigerant vapor generated bysaid evaporator is pressurized by said refrigerant compressor, and heatcarried by said pressurized refrigerant vapor may be utilized forheating feed water of said heat-recovery type steam generation boilerutilized for recovering by said steam turbine as power.
 6. A combinedpower plant according to claim 5 , wherein said evaporator of saidrefrigeration system is disposed within said intake-air cooling chamberof said intake-air cooling type gas turbine power equipment for coolingthe intake air, and wherein said refrigerant vapor leaving saidevaporator is compressed by said refrigerant compressor to thereby betransformed to a pressurized refrigerant vapor.
 7. A combined powerplant, comprising: intake-air cooling type gas turbine power equipment;a heat-recovery type steam generation boiler; steam turbine powergeneration equipment; and a condenser, said intake-air cooling type gasturbine power equipment comprising: a refrigeration system including anevaporator and a refrigerant compressor, an intake-air cooling chamberfor cooling air taken in from the atmosphere by said evaporator of saidrefrigeration system; an air compressor for compressing the air cooledin said intake-air cooling chamber to thereby produce compressed air; acombustor for burning a fuel supplied from an external system with thecompressed air produced by said air compressor to thereby produce acombustion gas; a gas turbine driven rotationally under the action ofsaid combustion gas produced by said combustor; and an electricgenerator operatively coupled to a rotor shaft of said gas turbine forgenerating electric energy, being driven through rotation of said rotorshaft, said heat-recovery type steam generation boiler serving forrecovering a quantity of heat carried by the combustion exhaust gasdischarged from said gas turbine of said gas turbine power equipment;said steam turbine power generation equipment comprising: a steamturbine driven rotationally under the action of ahigh-temperature/high-pressure steam produced by said heat-recovery typesteam generation boiler; and an electric generator operatively coupledto a rotor shaft of said steam turbine for generating electric energy,being driven through rotation of said rotor shaft; and said condenserserving for condensing to water the steam discharged from said steamturbine of said steam turbine power generation equipment, whereinrefrigerant vapor discharged from said evaporator of said refrigerationsystem is pressurized to a pressurized refrigerant vapor by saidrefrigerant compressor, said pressurized refrigerant vapor being fed tosaid condenser of said refrigeration system where said pressurizedrefrigerant vapor undergoes heat exchange with said condensate waterproduced by said condenser to thereby heat said condensed water whilesaid pressurized refrigerant vapor itself is condensed to a refrigerantliquid to be fed back to said evaporator, whereas said condensed wateras heated is fed to said heat-recovery type steam generation boiler. 8.A combined power plant according to claim 7 , wherein said evaporator ofsaid refrigeration system is disposed within said intake-air coolingchamber of said intake-air cooling type gas turbine power equipment forcooling the intake air, and said refrigerant vapor leaving saidevaporator is compressed by said refrigerant compressor to thereby betransformed to the pressurized refrigerant vapor.